Polishing system including a hydrostatic fluid bearing support

ABSTRACT

A polishing system such as a chemical mechanical belt polisher includes a hydrostatic fluid bearing that supports polishing pads and incorporates one or more of the following novel aspects. One aspect uses compliant surfaces surrounding fluid inlets in an array of inlets to extend areas of elevated support pressure around the inlets. Another aspect of the invention provides a hydrostatic bearing with spiral or partial cardiod drain grooves. This bearing has a non-uniform support pressure profile but provides a uniform average pressure to a wafer that is rotated relative to the center of the bearing.

CROSS REFERENCE TO RELATED APPLICATIONS

This is a divisional of U.S. patent application Ser. No. 09/187,532,filed Nov. 6, 1998, now U.S. Pat. No. 6,086,456 which is a divisional ofU.S. patent application Ser. No. 08/964,773, filed Nov. 5, 1997, nowU.S. Pat. No. 6,062,959.

BACKGROUND

1. Field of the Invention

This invention relates to polishing systems and particularly to chemicalmechanical polishing systems and methods using hydrostatic fluidbearings to support a polishing pad.

2. Description of Related Art

Chemical mechanical polishing (CMP) in semiconductor processing removesthe highest points from the surface of a wafer to polish the surface.CMP operations are performed on unprocessed and partially processedwafers. A typical unprocessed wafer is crystalline silicon or anothersemiconductor material that is formed into a nearly circular wafer aboutone to twelve inches in diameter. A typical processed or partiallyprocessed wafer when ready for polishing has a top layer of a dielectricmaterial such as glass, silicon dioxide, or silicon nitride or aconductive layer such as copper or tungsten overlying one or morepatterned layers that create projecting topological features on theorder of about 1 μm in height on the wafers surface. Polishing smoothesthe local features of the surface of the wafer so that ideally thesurface is flat or planarized over an area the size of a die formed onthe wafer. Currently, polishing is sought that locally planarizes thewafer to a tolerance of about 0.3 μm over the area of a die about 10 mmby 10 mm in size.

A conventional belt polisher includes a belt carrying polishing pads, awafer carrier head on which a wafer is mounted, and a support assemblythat supports the portion of the belt under the wafer. For CMP, thepolishing pads are sprayed with a slurry, and a drive system rotates thebelt. The carrier head brings the wafer into contact with the polishingpads so that the polishing pads slide against the surface of the wafer.Chemical action of the slurry and the mechanical action of the polishingpads and particles in the slurry against the surface of the wafer removematerial from the surface. U.S. Pat. Nos. 5,593,344 and 5,558,568describe CMP systems using hydrostatic fluid bearings to support a belt.Such hydrostatic fluid bearings have fluid inlets and outlets for fluidflows forming films that support the belt and polishing pads.

To polish a surface to the tolerance required in semiconductorprocessing, CMP systems generally attempt to apply a polishing pad to awafer with a pressure that is uniform across the wafer. A difficulty canarise with hydrostatic fluid bearings because the supporting pressure ofthe fluid in such bearings tends to be higher near the inlets and lowernear the outlets. Also, the pressure profile near an inlet falls off ina manner that may not mesh well with edges of the pressure profile anadjacent inlet so that pressure is not uniform even if the elevatepressure areas surrounding two inlets overlap. Accordingly, such fluidbearings can apply a non-uniform pressure when supporting a belt, andthe non-uniform pressure may introduce uneven removal of material duringpolishing. Methods and structures that provide uniform polishing aresought.

SUMMARY

Hydrostatic bearings include or employ one or more of the aspects of theinvention to support polishing pads for uniform polishing. In accordancewith one aspect of the invention a hydrostatic bearing support in apolishing system provides a fluid flow across fluid pads havingcompliant surfaces. The support pressure of a fluid film flow from afluid inlet and across a compliant pad drops more slowly with distancefrom the fluid inlet than does the support pressure over a rigid pad.Thus, an array of inlets where some or all of the inlets are surroundedby compliant pad can provide a more uniform pressure profile.

In accordance with another aspect of the invention, a fluid flow isvaried in a hydrostatic bearing that supports a polishing pad in contactwith a wafer or other object being polished. In one case, the fluid flowis periodically reversed by alternately connecting a fluid source toinlets so that fluid flows from the inlets to outlets and then switchingthe fluid source to the outlets so that fluid flows from the outlets toinlets. Reversing the fluid flow changes the bearing from aconfiguration in which support pressure is higher over the inlets to aconfiguration in which support pressure is higher over the outlets. On atime average basis, the support pressure is thus more uniform than ifthe fluid flow was not reversed. The changes in direction of fluid flowalso can introduce vibrations in the polishing pad thereby aidingpolishing. Another case of varying the fluid flow introduces pressurevariation in the fluid to transmit vibrational energy to the polishingpads. The pressure variation can be introduced, for example, via anelectrically controlled valve connected to a fluid source, an acousticcoupling that transfers acoustic energy to the fluid, or a mechanicalagitator in the fluid.

In accordance with another aspect of the invention, a hydrostaticbearing includes a large fluid cavity having a lateral size greater thanthe lateral size of a wafer (or other object) to be polished. The largefluid cavity can provide a large area of uniform support pressure. Inone embodiment of the invention, the large fluid cavity is surrounded bya support ring including fluid inlets connected to an independent fluidsource. The support ring is outside the area of support for polishingpads in contact with a wafer, but fluid flow from the inlets in thesupport ring is connected to fluid source having a pressure independentof the pressure in the large fluid cavity. Thus, changing fluid pressurein the support ring can change the fluid film thickness (and supportpressure) in the large cavity.

In accordance with yet another aspect of the invention, a hydrostaticbearing has a non-uniform support pressure profile but a wafer (or otherobject being polished) is moved so that average support pressure isconstant across the wafer when averaged over the range of motion. Onesuch hydrostatic bearing includes drain grooves that spiral from anouter region to a central region of the hydrostatic bearing. The spiraldrain grooves may follow, for example, a path that is a part of acardiod. Inlets arranged on concentric circles surrounding the centralregion have fluid pad areas with boundaries partially defined by thespiral drain grooves. These fluid pads extend along the spiral groovesso that the fluid pads associated with one ring of inlets extend toradii that overlap the radii of the fluid pads for adjacent rings ofinlets. The fluid pads are further disposed so that the same percentageof each circumferential path about the center of the bearing is on orover fluid pads. Thus, each point on a wafer that is rotated about thecenter of the bearing experiences the same average pressure. Thishydrostatic bearing can also be used with a support ring ofindependently controlled fluid inlets outside the outer region of thebearing.

In accordance with another aspect of the invention, a hydrostatic fluidbearing has constant fluid pressure at each fluid inlet and adjustssupport pressure by changing the height of one or more inlets and fluidpads with respect to the object being supported. In various embodimentsemploying this aspect of the invention, a hydrostatic fluid bearingincludes a set of inlet blocks where each inlet block includes one ormore fluid inlet (and associated fluid pad). The inlet blocks aremounted on a mechanical system that permits adjustments of the relativeheights of the inlet blocks. Such mechanical systems can be operated,for example, by air or hydraulic cylinders, piezoelectric transducers,or electrically power actuators or solenoids.

The various aspects of the invention can be employed alone or incombinations and will be better understood in view of the followingdescription and accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a belt polisher in accordance with an embodiment of theinvention.

FIG. 2 shows a plan view of a hydrostatic bearing for a belt support inthe belt polisher of FIG. 1.

FIGS. 3A, 3B, and 3C respectively show cross-sectional views of inletswith fluid pads having compliant surfaces for use in the fluid bearingof FIG. 2.

FIG. 4 shows a cross-sectional view of an outlet for the fluid bearingof FIG. 2.

FIG. 5 shows plots of support pressure verses distance from the centerof an inlet when the surrounding pad has a compliant surface or a rigidsurface.

FIG. 6 shows a perspective view of a hydrostatic bearing having a largefluid cavity that covers a supported polishing area.

FIG. 7 shows a perspective view of a hydrostatic bearing having spiralor cardiod fluid drain grooves.

FIG. 8 shows a perspective view of a hydrostatic bearing having inletswith adjustable relative heights for adjusting local fluid filmthicknesses and support pressures.

Use of the same reference symbols in different figures indicates similaror identical items.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

In accordance with the invention, hydrostatic bearings for supportingpolishing pads provide pressure profiles that contribute to uniformpolishing. Embodiments of the invention employ a number of inventiveaspects that can be used alone or in combinations. In accordance withone aspect of the invention, a hydrostatic bearing uses pads withcompliant rather than rigid surfaces. The compliant surface surroundinga fluid inlet changes the pressure profile surrounding the inlet andparticularly changes the rate of pressure drop with distance from theinlet. With the changed pressure profiles, broader uniform pressureregions are achieved and overlapping of pressure fields from multipleinlets can provide a more uniform pressure field that would rigidinlets.

In accordance with another aspect of the invention, the fluid flow in ahydrostatic bearing is modulated or periodically reversed to reduce theeffects of pressure difference between areas near fluid inlets and areasnear fluid outlets. The fluid flow rate and direction can be altered incontinuously or switched back and forth from a normal direction to areversed direction. During normal operation pressure is higher near theinlets and lower near the outlets in a fluid bearing. Reversing thefluid flow causes pressure to be higher near the outlets and lower nearthe inlets. The periodic changes in pressure can provide a more uniformtime-averaged material removal rate across the surface of a wafer beingpolished. Reversing or modulating the fluid flow can also introducevibrations in polishing pads that the bearing supports. The vibrationsimprove the rate and uniformity of polishing.

Yet another aspect of the invention provides fluid bearingconfigurations that provide uniform polishing. One such hydrostaticbearing includes a fluid inlet to a cavity that is large, e.g., largerthan the wafer or other object to be polished. The pressure field acrossthe cavity is nearly constant. Other hydrostatic bearings permitnon-uniformity in the support pressure profiles but limit thenon-uniformities according to the motion of wafers during polishing. Forexample, non-uniformities in support pressure are permitted if rotationof the wafer during polishing effectively averages the differentpolishing rates caused by the pressure differences. Exampleconfigurations and shapes of inlets, outlet, and channels for desirednon-uniformity in a hydrostatic bearing are described below. In oneembodiment, drain grooves defining boundaries of fluid pads follow aspiral or a partial cardiod path. The non-uniform pressure providesuniform polishing when a wafer is rotated about a central axis of thedrain grooves.

A further aspect of the invention provides a hydrostatic bearing supportthat attaches constant pressure sources to fluid inlets but adjusts thesupport pressure profile by changing film thickness in the hydrostaticbearing. In particular, fluid inlets in the hydrostatic bearing haveadjustable heights to vary fluid film thickness above individual inletsand fluid pads. The change in film thickness changes the supportpressure at the polishing pad and allows adjustments of the fluidbearing to improve uniformity of polishing.

Exemplary embodiments of polishing systems in which aspect of thisinvention can be employed are described in U.S. Pat. No. 5,957,764entitled “Modular Wafer Polishing Apparatus and Method”, which is herebyincorporated by reference herein in its entirety. FIG. 1 illustrates achemical mechanical polishing (CMP) system 100 which can employ thevarious aspects of the invention. CMP system 100 includes a wafercarrier head 110, a support assembly 140, and a belt 130 which isbetween head 110 and support assembly 140. Mounted on belt 130 arepolishing pads that are made of an abrasive material such as IC1400™available from Rodel, Inc. that is divided into areas (or lands) about½″×½″ in size. The width of belt 130 depends on the size of the wafer tobe polished; but for an 8-inch wafer, belt 130 is approximately 12inches in width and about 100 inches around. During polishing, belt 130and the polishing pads are conditioned with a slurry such asSEMI-SPHERSE 12™ available from Cabot Corporation.

A processed or unprocessed wafer to be polished is mounted on head 110with the surface to be polished facing the polishing pads on belt 130.Head 110 holds a wafer in contact with the polishing pads duringpolishing. Ideally, head 110 holds the wafer parallel to the surface ofthe polishing pads and applies a uniform pressure across the area of thewafer. Exemplary embodiments of wafer carrier heads are described in aco-filed U.S. patent application entitled “Wafer Carrier Head withAttack Angle Control for Chemical Mechanical Polishing”, Ser. No.08/965,033, now U.S. Pat. No. 6,080,040 which is hereby incorporated byreference herein in its entirety. Support 140 and head 110 presspolishing pads against the wafer mounted on head 110 with an averagepressure between 0 and about 15 psi and a typical polishing pressure of6 to 7 psi. A drive system 150 moves belt 130 so that the polishing padsslide against the surface of the wafer while head 110 rotates relativeto belt 130 and moves back and forth across a portion of the width ofbelt 130. Support 140 moves back and forth with head 110 so that thecenters of support 140 and head 110 remain relatively fixed.Alternatively, support 140 could be fixed relative to system 100 andhave a lateral extent that supports belt 130 under the range of motionof head 110. The mechanical action of the polishing pads and particlesin the slurry against the surface of the wafer and a chemical action ofliquid in the slurry remove material from the wafer's surface duringpolishing.

The polished wafer becomes uneven if the polishing consistently removesmore material from one portion of the wafer than from another portion ofthe wafer. Different rates of removal can result if the pressure of thepolishing pads on the wafer is higher or lower in a particular area. Forexample, if head 110 applies a greater pressure to a specific area ofthe wafer being polished or if support 140 applies a greater pressure toa specific area, a higher rate of material removal can result in thoseareas. The rotational and back and forth motion of head 110 relative tobelt 130 averages the variations in material removal rates. However, thedifferences in material removal can still result in annular variation inthe surface topology of the wafer after polishing. Embodiments of theinvention provide supports that reduce unevenness in the supportpressure and/or reduce the effect that an uneven support pressure has onpolishing.

FIG. 2 shows plan view of a hydrostatic bearing 200 that uses compliantpads 230 to form a hydrostatic bearing including an array of inlets 210with compliant pads 230 in accordance with an embodiment of theinvention. Hydrostatic bearing 200 includes a plate 240 on whichcompliant pads 230 are mounted. Plate 240 is made of a rigid materialsuch as aluminum or any other material of sufficient strength andchemical resistance to withstand the operating environment of a CMPsystem. Plate 240 is machined or otherwise formed to include inlets 210,outlets 220, and fluid conduits 215 and 225. During normal operation ofbearing 200, fluid conduits 215 and 225 respectively connect inlets 210to one or more fluid sources and outlets 225 to a fluid sink so thatfluid from inlets 210 flows across compliant pads 230 and provides thefluid film above compliant pads 230. The fluid film is preferably aliquid such as water and provides a support pressure to support a beltand/or polishing pads. A ridge 290 defines the boundaries of the bearingarea and is of sufficient width that a fluid film created by leakageover ridge 290 prevents direct contact between plate 240 and the belt.

FIGS. 3A, 3B, and 3C show cross-sectional views of compliant hydrostaticbearings 301, 302, and 303 that can be formed at each inlet 210 of FIG.2. In FIG. 3A, compliant bearing 301 has compliant pad 230 on a topsurface of rigid plate 240. Compliant pad 230 is an elastomer materialsuch as rubber or neoprene. For operation of bearing 200, a fluid suchas water at a pressure selected according to the leakage from bearing200 and the load that bearing 200 carries passes from inlet 210 througha hole 330 in the center of compliant pad 230. An inlet pressure between0 and 15 psi is typical when supporting a polishing pad duringpolishing. Pad 230 is sized according to the density of inlets inbearing 200 and in an exemplary embodiment are about 0.75″ in diameterfor an array of inlets separate by about 1.125″. In this exemplaryembodiment, the hole in pad 230 and inlet 210 at its widest is between0.020″ and 0.0625″ in diameter. Inlet 210 also includes orifice orrestriction 320 that restricts bearing stiffness, fluid flow rates, andother attributes of bearing 200.

Compliant bearing 301 provides a broader area of elevated supportpressure than do hydrostatic bearings having rigid surfaces. FIG. 5shows respective plots 510 and 520 of normalized pressure versus radiusfor a compliant bearing such as bearing 301 and a non-complianthydrostatic bearing having rigid surfaces. When a weight is supported byeither type of hydrostatic bearings, the support pressure is at itsmaximum pressure P over the fluid inlet, but outside the radius of thefluid inlet pressure drops. Plot 510 shows that pressure initially fallsoff much more slowly for a compliant bearing than for a non-compliantbearing. For example, at a radius about four times the radius of theinlet, the support pressure from the compliant bearing is about fourtimes the support pressure of the non-compliant bearing. The wider areaof significantly elevated pressure in a compliant bearing is believed tobe caused by deformation of compliant pad 210 changing the fluid filmthickness. Where pressure is highest, pad 210 is compressed whichincreases film thickness. Where pressure is lower, pad 210 expands todecrease film thickness and maintain pressure at a higher level thanwould a rigid surface. A wider area of significantly elevated pressurefor a compliant bearing reduces the size of low pressure areas betweeninlets 210 in an array such as in bearing 200 of FIG. 2. Thus, thesupport pressure profile of bearing 200 is more nearly constant.Additionally, individual inlets 210 can be placed close enough togetherin an array that elevated pressure areas overlap if drains 220 are lessthan 100% efficient at reducing pressure between inlets.

Compliant bearing 302 of FIG. 3B has compliant pad 210 counter sunk intoplate 240 so that in a relaxed state, a top surface of compliant pad 210is flush with the top surface of plate 240. Compliant bearing 303 ofFIG. 3C has compliant pad 210 further counter sunk into plate 240 sothat in a relaxed state, a top surface of compliant pad 210 is below thetop surface of plate. Bearings 302 and 303 have pressure profiles thatinclude features from both compliant and non-compliant hydrostaticbearings. The counter sinking of compliant pads 210 changes thestiffness of the fluid bearing. Accordingly, the amount of countersinking can be selected according to the desired stiffness for thebearing. Alternatively, a mounting that permits movement of the pad 230to change the depth of the fluid pocket over pad 230 to provide bearing200 with adjustable stiffness.

FIG. 4 shows a cross-sectional view of an embodiment of one of outlets220 of FIG. 2. Each outlet 220 is connected to one of conduits 225 whichare formed in plate 240 above or below conduits 215. During normaloperation, conduits 225 are connected to a fluid drain or sink.

In accordance with an aspect of the invention, fluid flow between inlets210 and outlets 220 is modulated by varying the fluid flow, e.g.,varying the pressure, flow rate, or the direction of fluid flow. Forexample, a fluid source and a fluid sink can be periodically switchedbetween a normal configuration where the fluid source is connected toconduits 215 and inlets 210 and the fluid sink is connected to conduits225 and outlets 220 and a reversed configuration where the fluid sink isconnected to conduits 215 and inlets 210 and the fluid source isconnected to conduits 225 and outlets 220. In the normal configuration,fluid films around inlets 210 provide the highest pressure to supportbelt 130, and lower pressures are near fluid outlets 220. Accordingly,the polishing pad areas that are above inlets 210 tend to remove wafermaterial faster than polishing pad areas over outlets 220, which canresult in uneven polishing. In the reverse configuration, highestsupport pressure regions form near outlets 220. Thus, in the reverseconfiguration, the polishing pad areas that are above outlets 220 tendto remove wafer material faster than polishing pad areas over inlets210. Periodically, switching between normal and reverse configurationstends to average the removal rates for all polishing pad areas. Suchswitching can be for all inlets 210 and outlets 220 simultaneously orsequentially in some pattern.

The array of inlets 210 and outlets 220 in bearing 200 is asymmetric inthat inlets 210 differ in sizes, number, and distribution from outlets220. A more symmetric fluid bearing having outlets of the same orsimilar size, number, and distribution as inlets may improve thesmoothing effects caused by periodically reversing the fluid flow.However, smoothing of the average pressure profile by periodicallyswitching the direction of fluid flow can be applied to any hydrostaticbearing and is not limit to a symmetric bearing configuration or to theconfiguration of bearing 200.

Another effect from periodically reversing the direction of fluid flowis that the changing pressures in support 140 or bearing 200 introducesoscillations or vibrations in belt 130 and the polishing pads. Dependingon vibration of polishing pads alone can provide superior polishing butat low polishing removal rates. The combined effects of belt rotationand vibrations are believed to improve polishing performance over beltrotation alone. Vibrations can be introduced in belt 130 by reversingfluid flow or by alternative methods such as modulation of fluid flow.For example, fluid flow rates or pressure can be changed smoothly, forexample, sinusoidally between the normal configuration to the reversedconfiguration. Modulating the fluid flow without reversing the directionof fluid flow can also introduce vibrations and can be achieved in anumber of ways. For example, an electric signal having the desiredfrequency can operate an electro-mechanical pressure controller (e.g., asolenoid valve) to modulate the pressure or flow rate at the desiredvibrational frequency. Alternatively, an acoustic coupler or amechanical agitator in the fluid can introduce acoustical energy ormechanical vibratory energy that is transmitted through the fluid tobelt 130 and the polishing pads. Such modulation or vibrational energytransfers can be uniform for all inlets 210 or individually controlledfor single inlets or groups of inlets. Yet another alternative forcausing vibration in the polishing pads is to vibrate support 140 toalter film thickness in the hydrostatic bearing. Embodiments of theinvention described below in regard to FIG. 8 provide control of thefilm thickness for individual or groups of inlets for better control ofvibrations introduced.

In accordance with another embodiment of the invention, FIG. 6 shows ahydrostatic fluid bearing 600 having a cavity 610 with a diameter largerthan that of the wafer to be polished. In particular, fluid in cavity610 supports the entire area of belt 130 where the wafer can contactpolishing pads. In the embodiment shown, bearing 600 is circular tomatch the shape of a wafer and moves during polishing to follow themotion of wafer. Alternatively, bearing 600 and cavity 610 can beelongated to support the polishing pads covering the entire range ofmotion of a wafer during polishing. Cavity 610 is surrounded by anelevated ridge or lip 615 that separates cavity 610 from a drain ring620. A fluid inlet 650 at the center of cavity 610 fills cavity 610 withfluid that overflows ridge 615 and drains out of bearing 600 throughdrain ring 620.

A retaining ring support 630 formed from fluid bearings associated withinlets 640 surrounds drain ring 620 and supports belt 130 around butoutside the area where the wafer contacts polishing pads duringpolishing. Bearing 600, thus, supports belt 130 entirely on fluid toprovide nearly frictionless and non-wearing bearing. A head on which thewafer is mounted may include a retaining ring that contacts the padsoverlying retaining ring support 630. The pressure to inlets 640 iscontrolled separately from the pressure to inlet 650 of cavity 610 andcan be adjusted for the pressure provided by the retaining ring on thewafer head. The pressure to retaining ring support 630 can also be usedto adjust the fluid film thickness and fluid depth in cavity 610. Fluidfrom retaining ring support 630 drains outward from bearing 600 to purgecontaminants such as slurry or residue from a polishing process awayfrom cavity 610.

Large cavity 610 has the advantage of providing a nearly uniformpressure for wafer support without regard for induced flow effects thatmotion of belt 130 causes. Induced flow effects can be changed byshaping cavity 610. In particular, the depth of cavity 610 can beadjusted, the shape of cavity 610 can be changed (e.g., the bottom ofcavity 610 can be flat or contoured), and additional inlets (or evenoutlets) can be introduced to cavity 610 to provide a favorable pressuredistribution. In the embodiment shown in FIG. 6, a bottom plate ofcavity 610 is mounted with adjustment screws that permit adjustment ofthe depth of cavity 610, and sensors 670 in cavity 610. Sensors 670 canbe distance sensors to measure the distance to belt 130 (or equivalentlythe film thickness) or pressure sensors to monitor the pressuredistribution. Control unit 180 uses the sensor measurements for possiblesystem adjustment such as changing cavity depth or the fluid pressure toinlet 650. Deeper pockets tend to handle induced flow effects moreefficiently, where shallower pockets are more affected by motion of thebelt. A suitable depth is typically about ½″.

As an alternative to attempting to provide uniform pressure, anon-uniform pressure distribution is acceptable if motion of a waferaverages the effects of the non-uniform pressure. For example, thepressure is non-uniform in a hydrostatic bearing including uniformpressure pads if drain groves in the support area provide a lowersupport pressure. However, if each point on a wafer is over a pressurepad for the same percentage of polishing time, the average appliedpressure is constant for all points on the wafer, and the sum or averageof polishing due to the non-uniform distribution of pressure results inuniform polishing.

FIG. 7 shows a plan view of a hydrostatic bearing 700 that has anon-uniform pressure distribution but provides uniform average pressureto a wafer when the wafer rotates relative to a center axis 750 ofbearing 700. Bearing 700 includes pressure pads 710, radial draingrooves 720, and cardiod drain grooves 730. Drain grooves 720 and 730,which connect to a fluid sink, define the boundaries of pressure pads710. In particular, each cardiod drain groove 730 follows the trace of apart (about half) of a cardiod so that some of the sides of pads 710 arealso sections of cardiods. More generally grooves 730 are not requiredto follow a partial cardiod path but alternatively follow a path thatspirals between an outer region and a central region of bearing 700. Astar shaped pressure pad 740 is in a region at the center 750 of bearing700 where grooves 720 and 730 (if extended) would intersect withinsufficient space between the grooves for fluid pads. Each fluid pad710 includes a fluid inlet 712, a cavity 714, and a landing 716. Fluidinlets 712 are located on concentric circles, and each fluid inlet 712is in an associated cavity 714 that is bounded by an associated landing716. Alternatively, multiple inlets could be provided in each cavity712. During normal CMP operations, a fluid flow from inlets 712 acrosslandings 714 to drain grooves 720 and 730 maintains a nearly constantpressure to a portion of belt 130 supported by the fluid film above pads710. Pressure to the portion of the belt over drain grooves 720 and 730is lower than the pressure over pads 710. Bearing 700 also includesinlets 762 and pressure pads 760 that form a retaining ring supportoutside the area under a wafer during polishing. Pads 760 provideadditional support for belt 130 to maintain desired film thickness inbearing 700. Fluid pressure to pads 710, 740, and 760 can be separatelycontrolled.

In accordance with an aspect of the invention, rotation of a wafer aboutcenter 750 causes each point on the wafer (not above center pad 740) tocross pressure pads 710, radial drain grooves 720, and cardiod draingrooves 730. Ideally, during a revolution, the percentage of time thatany point on the wafer spends over pads 710 is the same as thepercentage of time that every other point on the wafers spends over pads710. To achieve this goal, the total angular extent of pads 710 shouldbe the same for any circle centered about axis 750. Using cardiod orspiral grooves 730 helps achieve this goal. In particular, each pad 710can be classified by the circle intersecting the inlet 712 for the pad,and pads 710 having inlets 712 on a circle of inlets extend radially (oralong cardiod grooves 730) to overlap the radial extent of pads 710 withinlets 712 on a smaller circle and pads 710 with inlets 712 on a largercircle. Each circular path for a point on a wafer crosses pads 710 andcannot be entirely within a groove. Second, cardiod grooves 730 becomecloser to tangential with increasing distance from center axis 750, anda circumferential crossing distance of a cardiod groove 730 becomeslonger with increasing radius. Thus, the effective groove widthincreases to match increases in pad size, keeping the angular extent ofpads 710 roughly constant. Center pad 740 has a separate inlet pressurecontrol that can be adjusted so that pad 740 provides about the sameaverage pressure over a circle as do pads 710.

In accordance with another aspect of the invention, a hydrostaticsupport bearing uses a constant fluid pressure from a fluid source andat fluid inlets but changes the local fluid film thickness to adjust thesupport pressure profile of the hydrostatic support. In one embodimentof the invention, a mechanical system changes the fluid film thicknessby changing the relative heights of pads surrounding fluid inlets. Whilethe inlet fluid pressure is constant, the support pressure can beincreased in the area of a pad by moving the pad toward the belt todecrease the fluid film thickness above the pad. In a typicalhydrostatic bearing with an average fluid film thickness of about 0.001inches, height adjustments on the order of 0.0001 or 0.0002 inches givea range of support pressure suitable for adjustment of a polishingsystem.

FIG. 8 shows a perspective drawing of a portion of a hydrostatic bearing800 employing a movable inlet block 810 that contains inlets 812, pads814, and a fluid conduit 816 that connects inlets 812 to a constantpressure fluid source during operation of bearing 800. The full fluidbearing 800 contains six inlet blocks 810, and an associated deflectionbeam 820 supports each block 810. FIG. 8 shows only one inletblock—deflection beam pair to better illustrate structures underlyingdeflection beams 820. Spaces between inlet blocks 810 form fluid drains.

Each deflection beam 820 rests on contact point 830 and is mounted in aclevis mount 840. Contact points 830 apply upward forces to deflectassociated deflection beams 820 and move associated inlet blocks 810.The amount of deflection of (or equivalently the amount of force appliedto) each defection beam 820 determines the height of pads 814 and theoverlying fluid film thickness during operation of bearing 800.Independent control of contact points 830 provides independent controlof the heights of blocks 810. Each contact point 830 is on an associatedlever arm 860 having a pivot point 870. Independent actuators 850connect to lever arms 860 and apply torques to the associated lever arms860 to control the forces on deflection beams 220. Many alternativesystems for changing the height of an inlet block may be employed. Forexample, hydraulic or air cylinder or a piezoelectric actuator can bedirectly attached to move deflector beam 820 and/or inlet block 810.

During operation of fluid bearing 800, each conduit 816 is connected toa constant pressure fluid source so that the pressure of fluid exitinginlets 812 is nearly constant. The exiting fluid from inlets 814 formsfluid films in the areas of pads 814 and between blocks 810 and the beltor other surface supported by bearing 800. With constant inlet pressureand pad area, the support pressure depends on film thickness. A user ofa polishing system can manipulate actuators 850 to change height of pads814 and therefore change the film thickness in the neighborhood ofspecific pads and the support pressure in that neighborhood. Changingthe support pressure can correct uneven polishing for example, byincreasing or decreasing the support pressure in areas have too low ortoo high of a rate material removal.

In bearing 800, each inlet block 810 contains a linear array of inlets812 and pads 814. Fluid bearing 200 of FIG. 2 contains such lineararrays, and a set of inlet blocks 810 can form the inlet pattern ofbearing 200. Pads 814 can have either compliant (as in bearing 200) orrigid surfaces. Alternatively, any shape inlet block with any desiredpattern of inlets and pads can be mounted on a mechanical system thatraises or lowers the block. In particular, a bearing can include inletblocks that are concentric rings where each inlet block hasindependently adjustable height and a ring of inlets formed in theblock. The pads surrounding the such inlets can have any desired shapeincluding, for example, the shapes of pads 710 in fluid bearing 700 ofFIG. 7. A retaining ring support including pads 760 and inlets 762 canhave adjustable height (or fluid film thickness) or an independent fluidpressure from the remainder of the pads. In yet another alternativeembodiment, each pad in a hydrostatic fluid bearing has an independentlycontrolled height to allow user variation of film thickness for each padindividually.

Although the invention has been described with reference to particularembodiments, the description is only an example of the invention'sapplication and should not be taken as a limitation. For example,although the specific embodiments described are CMP belt polishingsystems for polishing semiconductor wafers, other embodiments includeother types of polishing systems that may be used for other purposes.For example, the hydrostatic bearings and supports described herein canbe employed in a mechanical polishing system having polishing pads on arotating disk or belt for polishing semiconductor wafers or optical ormagnetic disks for use in CD ROM drives and hard drives. Various otheruses, adaptations, and combinations of features of the embodimentsdisclosed are within the scope of the invention as defined by thefollowing claims.

We claim:
 1. A support for a polishing tool, the support including a fluid bearing that comprises: a plurality of fluid inlets for connection to a fluid source; a plurality of outlets for connection to a fluid sink; a plurality of compliant pads, wherein the inlets, the outlets, and the compliant pads are disposed so that when the inlets are connected to the fluid source and the outlets are connected to the fluid sink, a fluid film flows across the compliant pads.
 2. The support of claim 1, further comprising a plate in which the fluid inlets and fluid outlets are formed, wherein the compliant pads are mounted on a top surface of the plate.
 3. The support of claim 2, wherein the compliant pads are mounted above a top surface of the plate.
 4. The support of claim 2, wherein the compliant pads are flush mounted on a top surface of the plate.
 5. The support of claim 2, wherein the compliant pads are recessed in a top surface of the plate.
 6. The support of claim 2, wherein the compliant pads are mounted on a structure that permits adjustment of a level of the compliant pads relative to a top surface of the plate.
 7. The support of claim 1, wherein each compliant pad 230 comprises an elastomer material.
 8. The support of claim 7, wherein the elastomer material is selected from a group consisting of rubber and neoprene.
 9. A support for a polishing tool, including a hydrostatic fluid bearing that comprises: a plurality of pads, each pad including an inlet for connection to a fluid source; and a first drain groove for connection to a fluid sink, wherein the first drain groove separates pads from each other and follows a path spiraling between an outer region of the bearing and a center region of the bearing, the first drain groove defining edges of adjacent pads.
 10. The support of claim 9, wherein the path of the first drain groove has a partial cardiod shape.
 11. The support of claim 9, wherein the bearing further comprises one or more additional drain grooves, wherein each additional drain groove follows a path spiraling between the outer edge and the center region of the bearing and defines edges of adjacent pads separated by the additional drain groove.
 12. The support of claim 11, wherein the bearing further comprises a plurality of radial drain grooves extending in along a substantially straight path from the center region to the outer edge of the bearing.
 13. The support of claim 9, wherein the bearing further comprising a support ring surrounding the outer edge of the bearing.
 14. The support of claim 9, wherein the pads have a surface made of a compliant material.
 15. The support of claim 9, further comprising a mechanism for adjusting heights of one of the pads relative to another of the pads. 